Vehicle front suspension

ABSTRACT

A vehicle front suspension includes a lower suspension support structure, a transverse link, a steering knuckle and a lower knuckle breakaway structure. The transverse link has an inboard side and an outboard side, the inboard side being attached to the lower suspension support structure. The steering knuckle has an upper end, a lower end, and a wheel supporting section between the upper end and the lower end. The lower end is pivotally coupled to the outboard side of the transverse link. The lower knuckle breakaway structure is formed on the steering knuckle to release the steering knuckle from the transverse link upon application of a prescribed rearward directed force on the vehicle front suspension outboard of the lower suspension support structure.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a divisional application of U.S. patent application Ser. No. 13/794,006 filed on Mar. 11, 2013. The entire disclosure of U.S. patent application Ser. No. 13/794,006 is hereby incorporated herein by reference.

BACKGROUND

1. Field of the Invention

The present invention generally relates to a vehicle front suspension. More specifically, the present invention relates to a vehicle front suspension that includes at least one breakaway structure that facilitates release of a front wheel in response to an impact event in a frontal offset test.

2. Background Information

Vehicle body structures are regularly being redesigned to include structural features that absorb impact forces in response to impact events. Recently introduced impact event tests include a frontal offset test where a vehicle is provided with velocity in a vehicle longitudinal direction (forward momentum) such that a front corner of the vehicle (approximately 25 percent of the overall width of the vehicle) impacts a fixed, rigid barrier. FIGS. 1, 2 and 3 schematically show an example of a conventional vehicle V undergoing an impact event with a fixed barrier B in accordance with the frontal offset test.

FIG. 1 shows the conventional vehicle V approaching the rigid barrier B in the frontal offset test. FIG. 2 shows the conventional vehicle V just after initial impact with the rigid barrier B showing initial deformation and forward momentum being transformed into rotational displacement about the rigid barrier B. FIG. 3 shows the conventional vehicle V undergoing further deformation and rotation as a result of the impact event.

SUMMARY

One object is to provide breakaway structures that release a wheel of the vehicle such that the wheel moves out of a vehicle wheel well during an impact event of a frontal offset test.

In view of the state of the known technology, one aspect of the present disclosure is to provide a vehicle front suspension with a lower suspension support structure, a transverse link, a steering knuckle and a lower knuckle breakaway structure. The transverse link has an inboard side and an outboard side, the inboard side being attached to the lower suspension support structure. The steering knuckle has an upper end, a lower end, and a wheel supporting section between the upper end and the lower end. The lower end is pivotally coupled to the outboard side of the transverse link. The lower knuckle breakaway structure is formed on the steering knuckle to release the steering knuckle from the transverse link upon application of a prescribed rearward directed force on the vehicle front suspension outboard of the lower suspension support structure.

BRIEF DESCRIPTION OF THE DRAWINGS

Referring now to the attached drawings which form a part of this original disclosure:

FIG. 1 is a schematic view of a conventional moving vehicle showing its response to a small overlap test where a front corner of the vehicle is aligned with a fixed, rigid barrier for eventual impact with the barrier;

FIG. 2 is another schematic view of the conventional vehicle showing its response to the small overlap test at the beginning of an impact event with the front corner of the conventional vehicle impacting the barrier and beginning to undergo deformation;

FIG. 3 is still another schematic view of the conventional vehicle showing its response to the small overlap test with the conventional vehicle undergoing further deformation during the impact event;

FIG. 4 is a schematic view of a moving vehicle being subjected to a small overlap test where approximately 25 percent of the front of the vehicle aligned with a fixed, rigid barrier for eventual impact with the barrier in accordance with various embodiments;

FIG. 5 is another schematic view of the vehicle depicted in FIG. 4 showing an initial response to the impact event of the small overlap test with a front corner of the vehicle impacting the barrier and beginning to undergo deformation in accordance with the various embodiments;

FIG. 6 is still another schematic view of the vehicle depicted in FIGS. 4 and 5 showing a subsequent response to the impact event of the small overlap test with the moving vehicle undergoing further deformation during the impact event and with a front wheel moving laterally out of a wheel well of the vehicle in accordance with at least one embodiment;

FIG. 7 is side view of a front end of the vehicle showing portions of a front suspension in accordance with a first embodiment;

FIG. 8 is a top view of portions of the front suspension of the vehicle depicted in FIG. 7, with the front suspension removed from the vehicle showing an engine cradle, steering components, struts, steering knuckles and transverse links, the front suspension having a plurality of wheel releasing features, including an upper knuckle breakaway structure, a lower knuckle breakaway structure and a transverse link breakaway structure, in accordance with a first embodiment;

FIG. 9 is a perspective view of the portions of the front suspension of the vehicle depicted in FIG. 8, showing the engine cradle, the struts, the steering knuckles and the transverse links in accordance with the first embodiment;

FIG. 10 is an exploded perspective view of the portions of the front suspension of the vehicle depicted in FIGS. 8 and 9, showing the engine cradle, a strut, a steering knuckle and a transverse link in accordance with the first embodiment;

FIG. 11 is an exploded perspective view of the strut and the steering knuckle of the front suspension showing an upper knuckle breakaway structure in accordance with the first embodiment;

FIG. 12 is a side view of a lower end of the strut showing details of knuckle attachment flanges that include the upper knuckle breakaway structure in accordance with the first embodiment;

FIG. 13 is a perspective view of the strut and the steering knuckle of the front suspension fully assembled showing the upper knuckle breakaway structure in accordance with the first embodiment;

FIG. 14 is a perspective view of the strut and the steering knuckle of the front suspension showing the upper knuckle breakaway structure after an impact event releasing the steering knuckle from the lower end of the strut in accordance with the first embodiment;

FIG. 15 is an exploded perspective view of the steering knuckle and an outboard end of the transverse link of the front suspension showing a lower knuckle breakaway structure in accordance with the first embodiment;

FIG. 16 is a side view of a lower end of the steering knuckle showing details of the lower knuckle breakaway structure in accordance with the first embodiment;

FIG. 17 is a perspective view of the steering knuckle and the transverse link of the front suspension showing the lower knuckle breakaway structure after an impact event releasing the steering knuckle from the outboard end of the strut in accordance with the first embodiment;

FIG. 18 is a perspective view of the transverse link shown removed from the front suspension, the transverse link having an inboard side with a front attachment point and a rear attachment point, and an outboard side in accordance with the first embodiment;

FIG. 19 is a top view of the front suspension showing the front attachment point and the rear attachment point of the inboard side of the transverse link connected to the engine cradle defining a transverse link breakaway structure in accordance with the first embodiment;

FIG. 20 is another top view of the front suspension showing the front attachment point of the transverse link breaking away from the engine cradle in an initial response to the impact event in accordance with the first embodiment;

FIG. 21 is yet another top view of the front suspension showing the rear attachment point of the transverse link breaking away from the engine cradle in a further response to the impact event in accordance with the first embodiment;

FIG. 22 is a perspective view of a rear side section of the engine cradle showing a lower suspension support structure including an upper flange and a lower flange and a collar configured to receive the rear attachment point of the transverse link in accordance with the first embodiment;

FIG. 23 is a cross-sectional view of the collar and the rear attachment point of the transverse link showing details of a recess defined within the collar, the recess being dimensioned to receive and retain the rear attachment point of the transverse link in accordance with the first embodiment;

FIG. 24 is another cross-sectional view of the collar and the rear attachment point of the transverse link similar to FIG. 23, showing the transverse link in a released orientation with the rear attachment point being inserted into the recess of the collar, but being releasable from the collar in accordance with the first embodiment;

FIG. 25 is yet another cross-sectional view of the collar and the rear attachment point of the transverse link similar to FIGS. 23 and 24, showing the transverse link in an installed orientation with the rear attachment point being retained within the recess of the collar in accordance with the first embodiment;

FIG. 26 is an exploded perspective view of the strut and the steering knuckle of the front suspension showing an upper knuckle breakaway structure in accordance with a second embodiment;

FIG. 27 is a cross-sectional view of a lower end of the strut taken along the line 27-27 in FIG. 26, showing details of knuckle attachment flanges that include the upper knuckle breakaway structure in accordance with the second embodiment;

FIG. 28 is a perspective view of the strut and the steering knuckle of the front suspension fully assembled showing the upper knuckle breakaway structure in accordance with the second embodiment;

FIG. 29 is a perspective view of the strut and the steering knuckle of the front suspension showing the upper knuckle breakaway structure after an impact event releasing the steering knuckle from the lower end of the strut in accordance with the second embodiment;

FIG. 30 is an exploded perspective view of the strut and the steering knuckle of the front suspension showing an upper knuckle breakaway structure in accordance with a third embodiment;

FIG. 31 is a cross-sectional view of a lower end of the strut taken along the line 31-31 in FIG. 30, showing details of knuckle attachment flanges of the strut that include the upper knuckle breakaway structure in accordance with the third embodiment;

FIG. 32 is a perspective view of the strut and the steering knuckle of the front suspension fully assembled showing the upper knuckle breakaway structure in accordance with the third embodiment;

FIG. 33 is a perspective view of the strut and the steering knuckle of the front suspension showing the upper knuckle breakaway structure after an impact event releasing the steering knuckle from the lower end of the strut in accordance with the third embodiment;

FIG. 34 is an exploded perspective view of the strut and the steering knuckle of the front suspension showing an upper knuckle breakaway structure in accordance with a fourth embodiment;

FIG. 35 is a cross-sectional view of an upper end of the steering knuckle taken along the line 35-35 in FIG. 34, showing details of the upper end of the steering knuckle that includes the upper knuckle breakaway structure in accordance with the fourth embodiment;

FIG. 36 is a perspective view of the strut and the steering knuckle of the front suspension fully assembled showing the upper knuckle breakaway structure in accordance with the fourth embodiment;

FIG. 37 is a perspective view of the strut and the steering knuckle of the front suspension showing the upper knuckle breakaway structure after an impact event releasing the steering knuckle from the lower end of the strut in accordance with the fourth embodiment;

FIG. 38 is a perspective view of a transverse link shown removed from the front suspension, with an outboard side of the transverse link having a lower knuckle breakaway structure in accordance with a fifth embodiment;

FIG. 39 is another perspective view of the transverse link shown in FIG. 38 showing the lower knuckle breakaway structure after an impact event releasing the ball joint (and the steering knuckle) from the outboard side of the transverse link in accordance with the fifth embodiment;

FIG. 40 is a perspective view of a transverse link shown removed from the front suspension, the transverse link having a lower knuckle breakaway structure in accordance with a sixth embodiment;

FIG. 41 is another perspective view of the transverse link shown in FIG. 40 showing the lower knuckle breakaway structure after an impact event releasing the ball joint (and the steering knuckle) from the outboard side of the transverse link in accordance with the sixth embodiment;

FIG. 42 is an exploded perspective view of the steering knuckle and an outboard end of the transverse link of the front suspension showing a lower knuckle breakaway structure that includes a first cam surface on a lower portion of the steering knuckle and a second cam surface on an outboard side of the transverse link in accordance with a seventh embodiment;

FIG. 43 is a side view of the lower portion of the steering knuckle and the outboard side of the transverse link showing the first and second cam surfaces spaced apart from one another in accordance with the seventh embodiment;

FIG. 44 is another side view of the lower end of the steering knuckle and the outboard side of the transverse link showing the first and second cam surfaces of the lower knuckle breakaway structure contacting each other breaking a portion of the ball joint and releasing the steering knuckle from the transverse link in response to an impact event in accordance with the seventh embodiment;

FIG. 45 is a perspective view of the rear side section of the engine cradle showing the lower suspension support structure including the upper flange and the lower flange and a collar configured to receive the rear attachment point of the transverse link in accordance with an eighth embodiment;

FIG. 46 is a cross-sectional view of the engine cradle and the rear attachment point of the transverse link showing details of transverse link breakaway structure that includes a first cam surface formed on the transverse link and a second cam surface formed within the recess of the engine cradle in accordance with the eighth embodiment;

FIG. 47 is another cross-sectional view of the engine cradle and the rear attachment point of the transverse link similar to FIG. 46, showing the transverse link beginning to rotate about the rear attachment point such that the first and second cam surfaces begin to contact one another in response to an impact event in accordance with the eighth embodiment;

FIG. 48 is yet another cross-sectional view of the engine cradle and the rear attachment point of the transverse link similar to FIGS. 46 and 47, showing the transverse link breaking away from the engine cradle in response to continued contact between the first and second cam surfaces causing the fastener to break, releasing the transverse link from the engine cradle in accordance with the eighth embodiment; and

FIG. 49 is a perspective view of a transverse link that includes a front attachment point that includes a collar oriented horizontally in accordance with a ninth embodiment.

DETAILED DESCRIPTION OF EMBODIMENTS

Selected embodiments will now be explained with reference to the drawings. It will be apparent to those skilled in the art from this disclosure that the following descriptions of the embodiments are provided for illustration only and not for the purpose of limiting the invention as defined by the appended claims and their equivalents.

Referring initially to FIG. 4-10, a vehicle 10 is illustrated in accordance with a first embodiment. The vehicle 10 is provided with a plurality of wheel releasing features of a front suspension 12 of the vehicle 10 that are configured to release a wheel 14 in response to an impact event such as a small overlap test, such that the wheel 14 moves out of a wheel well 16 of the vehicle 10 during the impact event.

The Insurance Institute for Highway Safety (IIHS) has developed various tests where vehicles are provided with forward velocity and impacted against fixed, rigid barriers, like the rigid barrier B depicted in FIGS. 1-3. In the IIHS offset tests, the conventional vehicle C is aimed at the rigid barrier B such that approximately 25 percent of the front of the conventional vehicle C impacts the rigid barrier B. In other words, as indicated in FIGS. 1-3, only a front corner of the conventional vehicle C impacts the rigid barrier B. This IIHS test is also known as a frontal offset, narrow offset, or small overlap test. In such tests, a front bumper assembly of the conventional vehicle C is either not impacted, or undergoes only limited contact with the rigid barrier B during the impact event. Therefore, other structures at the front of the conventional vehicle C impact the rigid barrier B and absorb at least some of the kinetic energy associated with the rapid deceleration of the vehicle C that results from the impact event. When the vehicle C is provided with velocity and impacts the rigid barrier B, the rapid deceleration of the vehicle C transforms the kinetic energy associated with the mass and velocity of the vehicle C into deformation of the vehicle C and counter movement of the vehicle C. As is well known, kinetic energy is a function of mass times velocity. During the small offset test, the kinetic energy of the vehicle C is partially absorbed and partially transformed into other forms of kinetic energy, such as rotary motion. It should be understood that the kinetic energy associated with the forward velocity of the vehicle C (and in the description below) is transformed into an impacting force upon impact due to the rapid deceleration of the vehicle C. Consequently, hereinbelow, the terms impact force and impacting force as used herein correspond to the kinetic energy applied to the vehicle 10 during the small overlap test (the impact event), as described below with respect to the various embodiments.

The test is represented schematically in FIGS. 1-3. During the impact event, a variety of structures undergo deformation. This deformation is not explicitly depicted in FIGS. 2 and 3 with any degree of accuracy because such deformation varies from conventional vehicle to conventional vehicle, depending upon the overall design of the front structure of the conventional vehicle C. Instead, in FIG. 3, the conventional vehicle C is depicted with a generic degree of deformation as a result of the impact event. However, the conventional vehicles tested by the IIHS using the small overlap test have a relatively consistent response in that during the impact event with the rigid barrier B, the rear end R of the conventional vehicle C undergoes some rotation and swings laterally away from the rigid barrier B, as indicated in FIG. 3.

In other words, the forward velocity F_(F) of the conventional vehicle C as it moves is transformed upon impact with the rigid barrier B. The velocity F_(F) results in an equal and opposite reaction force acting on the vehicle C as the vehicle C suddenly decelerates. It is desirable to move the vehicle laterally outward from the barrier and avoid unnecessary loading of the dash-wall and/or A-pillar.

The wheel releasing features of the various embodiments described hereinbelow, when employed in the vehicle 10, are configured such that during an impact event, such as a small overlap test, the wheel 14 is consistently released from the front suspension 12 and moves laterally out of the wheel well 16 of the vehicle 10, as shown in FIGS. 4, 5 and 6. Specifically, in FIG. 4 the vehicle 10 is provided with a forward velocity V_(F1) and is subjected to a small overlap test where approximately 25 percent of the front of the vehicle aligned with the rigid barrier B. In FIG. 5 the vehicle 10 undergoes an initial response to the impact event of the small overlap test with a front corner of the vehicle impacting the barrier and beginning to undergo deformation. Hence, the forward velocity V_(F1) is reduced to a velocity V_(F2). In FIG. 6, the vehicle 10 undergoes a subsequent response to the impact event in that one or more of the vehicle releasing features has functioned properly and released the front wheel, such that the front wheel moves laterally out of a wheel well of the vehicle 10, and the forward velocity V_(F1) is reduced to a velocity V_(F3).

It should be understood from the drawings and the description herein, that during an impact event, such as the small overlap test, the reaction forces experienced by the vehicle 10 as it impacts the rigid barrier B are significant. These significant reaction forces are exponentially greater than the forces the structures of the vehicle 10 undergo during normal operating usage of the vehicle 10. In other words, the impact events referred to herein are intended as destructive tests. Further, the impact events of the small overlap tests are configured to impact the vehicle 10 such that the rigid barrier B impact the vehicle 10 at portions of the vehicle 10 outboard of a lower suspension support structure, which includes an engine cradle 46 that is described in greater detail below.

In the various embodiments described below, the vehicle 10 includes at least one, or a combination of two or more of a plurality of the wheel releasing features. The wheel releasing features are included in various structural elements that at least partially define the front suspension 12 shown in FIGS. 8-10, and described in greater detail below.

A brief description of the vehicle 10 is now provided with specific reference to FIG. 7. The vehicle 10 includes a variety of conventional elements, such as a front bumper assembly 18, a hood 20, fenders 22, a front side member 24, a dash wall 26, an A-pillar 28 and a sill 30.

The front bumper assembly 18 is a conventional assembly at the front of the vehicle 10. The hood 20 conceals an engine compartment and is typically hinged to move between a closed position (FIG. 7) and an open position (not shown). The fenders 22 are conventional elements that cover sides of the vehicle 10. As shown in FIG. 7, the depicted fender 22 at least partially defines the wheel well 16. The front side member 24 is a structural beam-like assembly that extends from the front bumper assembly 18 rearward to the dash wall 26 and further rearward under the passenger compartment of the vehicle 10. The front side member 24 is a conventional structure that extends in a vehicle longitudinal direction and supports a variety of elements of the vehicle 10, including the front suspension 12. The dash wall 26 extends laterally from side-to-side within the vehicle 10 dividing the passenger compartment from the engine compartment. The A-pillar 28 and the sill 30 are structural elements that at least partially define a front door opening and are rigidly coupled via intermediary structural elements to the front side member 24.

It should be understood that there are two front side members 24, two A-pillars 28 and two sills 30 in the vehicle 10. Only one side of the vehicle 10 is shown in FIG. 7 and hence only one of the front side members 24, one of the A-pillars 28 and one of the sills 30 are visible. Description of one of the front side members 24, one of the A-pillars 28 and one of the sills 30 applies equally to both sides of the vehicle 10. Since the various portions of the body structure of the vehicle 10 are conventional, further description is omitted for the sake of brevity.

As indicated in FIG. 7, the vehicle 10 also includes a strut tower 32. The strut tower 32 is a conventional structure within the engine compartment that is rigidly coupled to the front side member 24. The strut tower 32 defines at least part of an upper suspension support structure of the vehicle 10.

FIGS. 8-10 show the front suspension 12 removed from the front side member 24 and removed from the vehicle 10. The front suspension 12 includes a plurality of wheel releasing features, such as an upper knuckle breakaway structure 40, a lower knuckle breakaway structure 42 and a transverse link breakaway structure 44, which are described in greater detail below after a description of various other features of the front suspension 12. As used herein below, the term breakaway structure include frangible structures and frangible parts (parts that break or deform allowing release of connections between two separate elements) and also refers to parts or structures where two connected parts are released from connection with one another without breakage of either of the two connected parts.

As shown in FIGS. 8-10, the front suspension 12 includes the engine cradle 46 (a lower suspension support structure as mentioned above), struts 48, steering knuckles 50 and transverse links 52. Since the struts 48, the steering knuckles 50 and the transverse links 52 are identical (except that they are symmetrical mirror images of one another), description of only one will apply to both. Each of the wheels 14 is secured to a corresponding one of the steering knuckles 50 via conventional bearing structures (not shown) as indicated in FIG. 8. The arrow D in FIG. 8 indicates a forward longitudinal direction of the vehicle 10.

The engine cradle 46 includes a driver's side engine cradle member 54, a passenger's side engine cradle member 56 and a rear engine cradle member 58. The driver's side engine cradle member 54 includes an engine mount attachment portion, but otherwise includes all of the features the passenger's side engine cradle member 56 (they otherwise symmetrical mirror images of one another). Therefore, description of the driver's side engine cradle member 54 also applies to the passenger's side engine cradle member 56. The engine cradle 46 also includes a front engine cradle member 59 that extends between the driver's side engine cradle member 54 and the passenger's side engine cradle member 56. However, since the front engine cradle member 59 is a conventional portion of the engine cradle 46, further description is omitted for the sake of brevity.

The rear engine cradle member 58 extends between rearward ends of the driver's side engine cradle member 54 and the passenger's side engine cradle member 56. The rear engine cradle member 58 supports elements of the steering linkage of the front suspension 12. However, since the various elements of the steering linkage are conventional components, further description is omitted for the sake of brevity.

The engine cradle 46 also includes body attachment points 60, located at the four corners of the engine cradle 46, as indicated in FIGS. 8-10. The body attachment points 60 are located for removable attachment via fasteners (not shown) to the underside of the vehicle 10. More specifically, the body attachment points 60 attach to the front side members 24 of the vehicle 10. An engine assembly 62 is supported on the engine cradle 46. However, since the engine assembly 62 is a conventional component of the vehicle 10, further description is omitted for the sake of brevity.

As shown in FIG. 9, a rearward section of the driver's side engine cradle member 54 includes an upper flange 66 and a lower flange 68, with a recess 70 defined between the upper flange 66 and the lower flange 68. The upper flange 66, the lower flange 68 and the recess 70 basically define a lower suspension support structure of the engine cradle 46. More specifically, the transverse link 52 is installed within the recess 70 and attached to the driver's side engine cradle member 54 by fasteners that extend through apertures of the upper flange 66 and the lower flange 68. As is indicated in FIG. 9, the transverse link 52 is attached at a first location 72 and a second location 74 of the lower suspension support structure by fasteners F₁. The first location 72 defines a front link attachment point for the transverse link 52 and the second location 74 defines a rear link attachment point for the transverse link 52.

A description of the strut 48 is now provided with specific reference to FIG. 11. The strut 48 includes an upper end 80 and a lower end 82. As indicated in FIG. 7, the upper end 80 is removably fastened to the strut tower 32 (the upper suspension support structure) in a conventional manner. The lower end 82 is configured to pivot relative to the upper end 80 in order to facilitate steering of the vehicle 10. The lower end 82 includes a pair of knuckle attachment flanges 84, as shown in FIG. 11. Each of the knuckle attachment flanges 84 includes a pair of apertures A that receive the fasteners F₂.

In the first embodiment, the knuckle attachment flanges 84 define the upper knuckle breakaway structure 40. Specifically, the upper knuckle breakaway structure 40 is defined by an area on each of the knuckle attachment flanges 84 adjacent to each of the apertures A. Each of the knuckle breakaway structures 40 are frangible parts that are inclined downward in a vehicle outboard direction from the apertures A (fastener receiving openings). Each of the upper knuckle breakaway structures 40 has a first thickness T₁, as indicated in FIG. 12. Each of the knuckle attachment flanges 84 has a second thickness T₂, with the second thickness T₂ being greater than the first thickness T₁. It should be understood from the drawings and the description herein that the thickness T₁ is not necessarily a reduction in thickness as compared to conventional struts. Rather, the thickness T₂ can be increased relative to conventional struts. In other words, the upper knuckle breakaway structures 40 are frangible parts. The lower end 82 of the strut 48 is therefore connected to an upper end 88 of the steering knuckle 50 by the upper knuckle breakaway structures 40 which have a predetermined frangible part that releases the upper end 88 of the steering knuckle 50 from the strut 48 upon application of a prescribed rearward directed force on at least one of the engine cradle 46 (the lower suspension support structure) and the steering knuckle 50.

Thus, during an impact event as the small overlap test, release of the wheel 14 from the wheel well 16 is facilitated by the breakage of the knuckle attachment flanges 84 at the upper knuckle breakaway structures 40. Specifically, FIG. 13 shows the strut 48 attached to the steering knuckle 50 by the fasteners F₂ during operation of the vehicle 10. During operation of the vehicle 10 (driving), the strut 48 and the steering knuckle 50 are rigidly secured to one another. During the impact event, if breakage occurs, the upper knuckle breakaway structures 40 deform, releasing the fasteners F₂ and the steering knuckle 50 (along with the wheel 14) such that they are free to move away from the strut 48 and out of the wheel well 16, as shown in FIG. 14.

As shown in FIG. 15, the steering knuckle 50 includes an upper end 88, a lower end 90 and a wheel supporting section 92. The upper end 88 defines an attachment collar that includes a pair of apertures dimensioned to receive the fasteners F₂ for attachment to the strut 48 in a manner described above and shown in FIG. 13. The pair of apertures in the upper end 88 of the steering knuckle 50 defines a strut attachment portion. As shown in FIG. 15, the lower end 90 includes a ball joint receiving aperture 94 dimensioned to receive a ball joint 96 of the transverse link 52. The lower end 90 also includes the lower knuckle breakaway structure 42. As shown in FIG. 16, the lower knuckle breakaway structure 42 has a thickness T₃ that is less than the thickness T₄ of adjacent areas of the lower end 90 of the steering knuckle 50. Put another way, the cross-sectional area of the lower knuckle breakaway structure 42 is less than the cross-sectional area of the adjacent areas of the lower end 90 of the steering knuckle 50.

The wheel supporting section 92 is provided with a hub and bearing structure (shown in FIGS. 13 and 14) such that the wheel 14 is coupled to the wheel supporting section 92 in a conventional manner.

During operation of the vehicle 10 (driving), the steering knuckle 50 and the transverse link 52 are pivotally secured to one another by the ball joint 96. During an impact event such as the small overlap test, since the lower knuckle breakaway structure 42 has a thickness T₃ less than the thickness T₄, if breakage occurs, the lower knuckle breakaway structures 42 breaks, releasing the steering knuckle 50 from the transverse link 52. Put another way, since the cross-sectional area of the lower knuckle breakaway structure 42 is less than the cross-sectional area of the adjacent areas of the lower end 90 of the steering knuckle 50, if breakage occurs, the lower knuckle breakaway structures 42 breaks, releasing the steering knuckle 50 from the transverse link 52. Hence, the steering knuckle 50 (and the wheel 14) are free to move away from the transverse link 52 (and out of the wheel well 16), as shown in FIG. 17.

The transverse link breakaway structure 44 will now be described with specific reference to FIGS. 18 thru 25. As shown in FIG. 18, the transverse link 52 includes a front end 98, a rear end 100, an inboard side 102 and an outboard side 104. The inboard side 102 includes a front attachment point 110 and a rear attachment point 112. The outboard side 104 includes a knuckle attachment point 114, which includes the ball joint 96.

The front attachment point 110 of the transverse link 52 includes a collar 116 that is attached to the engine cradle 46 (the lower suspension supporting portion) at the first location 72 (the front link attachment point) by one of the fasteners F₁. The collar 116 is a flexible coupling collar that includes a rubber or polymeric sleeve (not shown) that allows the transverse link 52 undergo vertical oscillations in response to various driving conditions in a conventional manner. Since such collars are conventional, further description is omitted for the sake of brevity.

The collar 116 and corresponding one of the fasteners F₁ define a front connection structure of the transverse link 52 connecting the front end 98 of the transverse link 52 to engine cradle 46 at the first location 72, as indicated in FIG. 19. As will be understood in the drawings and the description herein below, the fastener F₁ at the first location 72 is a frangible part that is configured to break in response to the impact event.

The rear attachment point 112 of the transverse link 52 is coupled to the engine cradle 46 at the second location 74 (the rear link attachment point) by the other of the fasteners F₁ in a manner that is described in greater detail below. The knuckle supporting section 114 is attached to the steering knuckle 50 via the ball joint 96.

As shown in FIG. 18, the rear attachment point 112 of the transverse link 52 includes a crescent shaped attachment portion 120. As indicated in FIG. 22, a collar 122 is inserted into the recess 70 between the upper flange 66 and the lower flange 68 (the lower suspension support structure). As shown in FIGS. 23-25, the collar 122 includes an opening 124 that exposes an arcuate shaped recess 126. The opening 124 is dimensioned such that the collar 122 passes into the arcuate shaped recess 126, as indicated in FIG. 24. Thereafter, the transverse link 52 is pivoted into an installed orientation such that the transverse link 52 is retained by the collar 122, as shown in FIG. 25. With the collar 122 installed to the second location 74 of the engine cradle 46, as shown in FIGS. 19 and 25, the rear attachment point 112 secures the transverse link 52 in position relative to the engine cradle 46 during normal driving operation of the vehicle 10. As is explained further below, the relationship between the collar 122 and the rear attachment point 112 of the transverse link 52 define a rear link breakaway structure that allows the transverse link 52 to be released from the engine cradle 46 in response to an impact event, such as the small overlap test.

FIG. 19 shows the transverse link 52 installed to the engine cradle 46 in the installed orientation with the fastener F₁ at the first location 72 retaining the front attachment point 110 of the transverse link 52 to the engine cradle 46. Further, the collar 122 and the other of the fasteners F₁ retain the rear attachment point 112 of the transverse link at the second location 74 of the engine cradle 46. As well, although not shown in FIG. 19, the ball joint 96 is installed to the steering knuckle 50, retaining the knuckle supporting section 114 of the outboard side 104 of the transverse link 52 to the steering knuckle 50.

During normal operation of the vehicle 10, the strut 48 can undergo vertical oscillations as a result of uneven road surfaces, the steering knuckle 50 can pivot about the strut 48 in response to steering operations of the vehicle 10 and the outboard side 104 of the transverse link 52 can undergo vertical oscillations as a result of uneven road surfaces due to the conventional flexing of the collar 116 and the collar 122.

During an impact event, such as the small overlap test, the transverse link 52 can breakaway from the engine cradle 46, as described now with reference to FIGS. 20 and 21. Specifically, when an impacting force such as a prescribed rearward directed force F_(R) acts on one or all of the strut 48, the steering knuckle 50 and/or the transverse link 52, the fastener F₁ at the first location 72 serves a front link breakaway structure. Specifically, as indicated in FIG. 20, upon application of the prescribed rearward directed force F_(R), the fastener F₁ at the first location 72 breaks (the fastener F₁ at the first location 72 is a frangible part). As the impact event progresses, the transverse link 52 pivots relative to the second location 74, as shown in FIG. 20. Thus, the transverse link 52 pivots from the installed orientation (FIGS. 19 and 25) to the release orientation (FIGS. 20 and 24). The transverse link 52 is no longer retained by the collar 122 and the crescent shaped attachment portion 120 can slip out of the opening 124 of the collar 122, as indicated in FIGS. 21 and 23.

During the impact event, the lower knuckle breakaway structure 42, as described above, breaks away allowing the knuckle supporting section 114 of the transverse link 52 to be released from the steering knuckle 50. At the same time, it is also possible for the upper knuckle breakaway structure 40 to release the steering knuckle 50 from the strut 48, as described above. Consequently, the steering knuckle 50 and the wheel 14 are released and can exit the wheel well 16 of the vehicle 10.

In the first embodiment described above, the front suspension 12 is described as including all three of the breakaway features, the upper knuckle breakaway structure 40, the lower knuckle breakaway structure 42 and the transverse link breakaway structure 44. However, it should be understood from the drawings and the description herein that each of the breakaway features can be used independently or in combination with only one of the other two breakaway features. Specifically, the upper knuckle breakaway structure 40 can be employed without one or the other of the lower knuckle breakaway structure 42 and the transverse link breakaway structure 44. Similarly, the lower knuckle breakaway structure 42 can be employed without one or the other of the upper knuckle breakaway structure 40 and the transverse link breakaway structure 44, and the transverse link breakaway structure 44 can be employed without one or the other of the upper knuckle breakaway structure 40 and the lower knuckle breakaway structure 42.

Further, various alternative embodiments of each of the upper knuckle breakaway structure 40, the lower knuckle breakaway structure 42 and the transverse link breakaway structure 44, are described below. The upper knuckle breakaway structure 40 of the first embodiment can be replaced with one of the alternative upper knuckle breakaway structure embodiments described below. The lower knuckle breakaway structure 42 of the first embodiment can be replaced with one of the alternative lower knuckle breakaway structure embodiments described below. Further, the transverse link breakaway structure 44 can be replaced with one of the alternative transverse link breakaway structure embodiments described below.

Second Embodiment

Referring now to FIGS. 26-29, an upper knuckle breakaway structure 140 in accordance with a second embodiment will now be explained. In view of the similarity between the first and second embodiments, the parts of the second embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the second embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the second embodiment, the strut 48 and the steering knuckle 50 are identical to the first embodiment, except that the upper knuckle breakaway structures 40 has been eliminated and replaced with the upper knuckle breakaway structures 140. As shown in FIGS. 26-29, the upper knuckle breakaway structures 140 are formed such that they extend upright along the surfaces of the knuckle attachment flanges 84 adjacent to an upright part of the strut 48. Each of the knuckle breakaway structures 140 is formed with the thickness T₁ which is less than the thickness T₂ of the remainder of the knuckle attachment flanges 84. As shown in FIG. 29, in response to the impact event, the majority of the knuckle attachment flanges 84 breakaway from the lower end of the strut 46.

Third Embodiment

Referring now to FIGS. 30-33, an upper knuckle breakaway structure 140 a in accordance with a third embodiment will now be explained. In view of the similarity between the first and third embodiments, the parts of the third embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the third embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the third embodiment, the strut 48 and the steering knuckle 50 are identical to the first embodiment, except that the upper knuckle breakaway structures 40 has been eliminated and replaced with the upper knuckle breakaway structure 140 a. As shown in FIGS. 30-33, the upper knuckle breakaway structures 140 a are formed such that they extend upright along a mid-section of the surfaces of the knuckle attachment flanges 84. Each of the upper knuckle breakaway structures 140 a is formed with the thickness T₁ which is less than the thickness T₂ of the remainder of the knuckle attachment flanges 84. As shown in FIG. 33, in response to the impact event, a portion of the knuckle attachment flanges 84 breakaway from the lower end of the strut 46.

Fourth Embodiment

Referring now to FIGS. 34-37, an upper knuckle breakaway structure 240 in accordance with a fourth embodiment will now be explained. In view of the similarity between the first and fourth embodiments, the parts of the fourth embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the fourth embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the fourth embodiment, the strut 48 and the steering knuckle 50 include all the features described above with respect to the first embodiment, except that the upper knuckle breakaway structures 40 has been eliminated from the knuckle attachment flanges 84 of the strut 48 and replaced with the upper knuckle breakaway structure 240 formed at the upper end 88 of the steering knuckle 50. As shown in FIGS. 34-37, the upper knuckle breakaway structure 240 is formed at the upper end 88 of the steering knuckle 50. The upper knuckle breakaway structure 240 has a thickness T_(1A) which is less than the thickness T_(2A) of the remainder of the upper end 88 of the steering knuckle 50. Consequently, the cross-sectional area of the upper knuckle breakaway structure 240 is less than the remainder of the upper end of the steering knuckle 50. As shown in FIG. 37, in response to the impact event, a portion of the upper end 88 of the steering knuckle 50 remains attached to the attachment flanges 84 of the strut 46.

Fifth Embodiment

Referring now to FIGS. 38-39, a lower knuckle breakaway structure 242 in accordance with a fifth embodiment will now be explained. In view of the similarity between the first and fifth embodiments, the parts of the fifth embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the fifth embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the fifth embodiment, the transverse link 52 and the collar 122 are replaced with a transverse link 252 and collar 122 a. The transverse link 252 includes a rear attachment point 112 a with the conventional collar 122 a. Hence, there is no breakaway feature at the rear attachment point 112 a.

The transverse link 252 includes all of the other features of the transverse link 52 of the first embodiment, such as the front attachment point 110 and knuckle supporting section 114, with the ball joint 96. However, adjacent to the knuckle supporting section 114 of the transverse link 252, the transverse link 252 is formed with the lower knuckle breakaway structure 242. The transverse link 252 is provided with reinforcements (as compared to a conventional transverse link) throughout its overall structure, except at the lower knuckle breakaway structure 242. Therefore, the lower knuckle breakaway structure 242 defines a frangible part. Consequently, as indicated in FIG. 39, in response to the impact event, the knuckle supporting section 114 and ball joint 96 breakaway from the remainder of the transverse link 252, allowing the steering knuckle (not shown) and the wheel 14 (not shown) to eject from the wheel well 16 of the vehicle 10 during the impact event.

Sixth Embodiment

Referring now to FIGS. 40-41, a lower knuckle breakaway structure 342 in accordance with a sixth embodiment will now be explained. In view of the similarity between the first and sixth embodiments, the parts of the sixth embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the sixth embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the sixth embodiment, the transverse link 52 and the collar 122 are replaced with a transverse link 352 and the collar 122 a. The transverse link 352 includes the rear attachment point 112 a with the conventional collar 122 a. Hence, there is no breakaway feature at the rear attachment point 112 a.

The transverse link 352 includes all of the other features of the transverse link 52 of the first embodiment, such as the front attachment point 110 and knuckle supporting section 114, with the ball joint 96. However, between the inboard side 102 and the outboard side 104, the transverse link 352 is formed with the lower knuckle breakaway structure 342. The transverse link 352 is provided with reinforcements (as compared to a conventional transverse link) throughout its overall structure, except at the lower knuckle breakaway structure 342. Therefore, the lower knuckle breakaway structure 342 defines frangible parts of the transverse link 352. Consequently, as indicated in FIG. 41, in response to the impact event, the knuckle supporting section 114 and ball joint 96 breakaway from the remainder of the transverse link 352, allowing the steering knuckle (not shown) and the wheel 14 (not shown) to eject from the wheel well 16 of the vehicle 10 during the impact event.

Seventh Embodiment

Referring now to FIGS. 42-44, a lower knuckle breakaway structure 442 in accordance with a seventh embodiment will now be explained. In view of the similarity between the first and seventh embodiments, the parts of the seventh embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the seventh embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the seventh embodiment, the lower end 90 of the steering knuckle 50 is modified to include a first cam surface C₁. Further, the knuckle supporting section 114 of the transverse link 52 is modified to include a second cam surface C₂. As is well known, the ball joint 96 is a structural member that connects to the steering knuckle 50 and allows the steering knuckle 50 to pivot about a vertical axis defined by the ball joint 96 such that the steering knuckle 50 can pivot for steering operations of the vehicle 10. The first cam surface C₁ and the second cam surface C₂ are positioned such that during steering operations of the vehicle 50, the first cam surface C₁ and the second cam surface C₂ do not contact one another, as indicated in FIG. 43. However, in response to an impact event where at least one member of the front suspension 12 has broken away from the engine cradle 46, the steering knuckle 50 and the transverse link 52 can undergo relative rotation with respect to one another such that the first cam surface C₁ and the second cam surface C₂ contact one another, forcing the transverse link 52 to move downward and away from the steering knuckle 50, as indicated in FIG. 44. This downward movement of the transverse link 52 can cause the ball joint 96 to pull out of the steering knuckle 50 or cause the ball joint 96 to break, as shown in FIG. 44, thereby allowing the steering knuckle 50 and the wheel 14 (not shown) to eject from the wheel well 16 of the vehicle 10 during the impact event.

Eighth Embodiment

Referring now to FIGS. 45-48, a transverse link breakaway structure 344 in accordance with an eighth embodiment will now be explained. In view of the similarity between the first and eighth embodiments, the parts of the eighth embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the eighth embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

In the eighth embodiment, the transverse link 52 of the first embodiment is replaced with a transverse link 52 a that includes a full ring structure at the rear attachment point 112 a and a first cam surface C₃. A conventional collar is installed within the full ring structure of the rear attachment point 112 a and the fastener F₁ attaches the transverse link 52 a to the engine cradle 46 at the second location 74. As shown in FIGS. 46-48, the first cam surface C₃ faces the engine cradle 46 within the recess 70. Also, in the eighth embodiment, the engine cradle 46 is slightly modified by the inclusion of a second cam surface C₄ formed within the recess 70, as is also shown in FIGS. 46-48.

With the transverse link 52 a in an installed orientation depicted in FIG. 46, the first cam surface C₃ and the second cam surface C₄ are spaced apart from one another. However, in response to an impact event, when the fastener F₁ at the first location 72 serves as a frangible part and breaks, the transverse link 52 a begins to pivot about the fastener F₂ at the second location 74, as indicated in FIG. 47. As is further shown in FIG. 47, the first cam surface C₃ and the second cam surface C₄ begin to contact one another. Further rotation of the transverse link 52 a during the impact event causes the first cam surface C₃ and the second cam surface C₄ to press against one another forcing the rear attachment point 112 a of the transverse link 52 to exert a force on the fastener F₁ at the second location 74, causing the fastener F₁ at the second location 74 to break (a frangible portion), thereby allowing the transverse link 52 a to be released from the engine cradle 46.

Ninth Embodiment

Referring now to FIG. 49, a transverse link 52 b in accordance with a ninth embodiment will now be explained. In view of the similarity between the first and ninth embodiments, the parts of the ninth embodiment that are identical to the parts of the first embodiment will be given the same reference numerals as the parts of the first embodiment. Moreover, the descriptions of the parts of the ninth embodiment that are identical to the parts of the first embodiment may be omitted for the sake of brevity.

The transverse link 52 b includes all of the features of the transverse link 52 of the first embodiment, except that the front attachment point 110 of the first embodiment is replaced with a modified front attachment point 110 a. More specifically, the transverse link 52 b includes the following features of the transverse link 52, for example, the front end 98, the rear end 100, the inboard side 102, the outboard side 104, the rear attachment point 112 with the crescent shaped attachment portion 120 and the knuckle supporting section 114 with the ball joint 96.

However, in the first embodiment, the fasteners F₁ at the first location 72 and the second location 74 of the engine cradle 46 are vertically oriented. In the ninth embodiment, the front attachment point 110 a is oriented such that a corresponding fastener is horizontally oriented. Otherwise, the transverse link 52 b is identical to the transverse link 52 b of the first embodiment.

The vehicle 10 includes a variety of elements and features are conventional components that are well known in the art. Since these elements and features are well known in the art, these structures will not be discussed or illustrated in detail herein. Rather, it will be apparent to those skilled in the art from this disclosure that the components can be any type of structure and/or programming that can be used to carry out the present invention.

GENERAL INTERPRETATION OF TERMS

In understanding the scope of the present invention, the term “comprising” and its derivatives, as used herein, are intended to be open ended terms that specify the presence of the stated features, elements, components, groups, integers, and/or steps, but do not exclude the presence of other unstated features, elements, components, groups, integers and/or steps. The foregoing also applies to words having similar meanings such as the terms, “including”, “having” and their derivatives. Also, the terms “part,” “section,” “portion,” “member” or “element” when used in the singular can have the dual meaning of a single part or a plurality of parts. Also as used herein to describe the above embodiment(s), the following directional terms “forward”, “rearward”, “above”, “downward”, “vertical”, “horizontal”, “below” and “transverse” as well as any other similar directional terms refer to those directions of a vehicle equipped with the vehicle front suspension. Accordingly, these terms, as utilized to describe the present invention should be interpreted relative to a vehicle equipped with the vehicle front suspension.

The term “configured” as used herein to describe a component, section or part of a device includes hardware and/or software that is constructed and/or programmed to carry out the desired function.

The terms of degree such as “substantially”, “about” and “approximately” as used herein mean a reasonable amount of deviation of the modified term such that the end result is not significantly changed.

While only selected embodiments have been chosen to illustrate the present invention, it will be apparent to those skilled in the art from this disclosure that various changes and modifications can be made herein without departing from the scope of the invention as defined in the appended claims. For example, the size, shape, location or orientation of the various components can be changed as needed and/or desired. Components that are shown directly connected or contacting each other can have intermediate structures disposed between them. The functions of one element can be performed by two, and vice versa. The structures and functions of one embodiment can be adopted in another embodiment. It is not necessary for all advantages to be present in a particular embodiment at the same time. Every feature which is unique from the prior art, alone or in combination with other features, also should be considered a separate description of further inventions by the applicant, including the structural and/or functional concepts embodied by such features. Thus, the foregoing descriptions of the embodiments according to the present invention are provided for illustration only, and not for the purpose of limiting the invention as defined by the appended claims and their equivalents. 

What is claimed is:
 1. A vehicle front suspension comprising: a lower suspension support structure; a transverse link having an inboard side and an outboard side, the inboard side attached to the lower suspension support structure; a steering knuckle having an upper end, a lower end, and a wheel supporting section between the upper end and the lower end, with the lower end pivotally coupled to the outboard side of the transverse link; and a lower knuckle breakaway structure formed on the steering knuckle to release the steering knuckle from the transverse link upon application of a prescribed rearward directed force on the vehicle front suspension outboard of the lower suspension support structure.
 2. The vehicle front suspension according to claim 1, wherein at least the wheel supporting section is free from connection to the transverse link upon release of the steering knuckle from the transverse link.
 3. The vehicle front suspension according to claim 2, wherein the lower knuckle breakaway structure includes a frangible portion formed on the steering knuckle.
 4. The vehicle front suspension according to claim 2, wherein the frangible portion is located between the wheel supporting section and the lower end of the steering knuckle, such that the upper end and the wheel supporting section are released from the lower end, and the lower end remains attached to the transverse link upon application of the prescribed rearward directed force.
 5. The vehicle front suspension according to claim 1, wherein the steering knuckle is coupled to the transverse link by a ball joint, and the lower knuckle breakaway structure includes a cam structure configured to release the ball joint upon rotation of the steering knuckle relative to the transverse link.
 6. The vehicle front suspension according to claim 5, wherein the cam structure of the lower knuckle breakaway structure comprises a first cam surface on the outboard side of the transverse link and a second cam surface on the lower portion of the steering knuckle, with the second cam surface travelling along the first cam surface to cause vertical movement of the steering knuckle relative to the transverse link as the steering knuckle rotates relative to the transverse link.
 7. The vehicle front suspension according to claim 6, wherein the ball joint is configured to break upon prescribed vertical movement of the steering knuckle relative to the transverse link.
 8. The vehicle front suspension according to claim 5, wherein the upper end, the lower end, and the wheel supporting section are free from connection to the transverse link upon release of the steering knuckle from the transverse link.
 9. The vehicle front suspension according to claim 1, further comprising: an upper suspension support structure; a strut having an upper end coupled to the upper suspension support structure, and a lower end coupled to the upper end of the steering knuckle; and an upper knuckle breakaway structure configured to release the steering knuckle from the strut upon application of the prescribed rearward directed force, such that at least the wheel supporting section is free from connection to the upper suspension support structure and the lower suspension support structure.
 10. A vehicle front suspension comprising: a lower suspension support structure; a transverse link having an inboard side and an outboard side, the inboard side attached to the lower suspension support structure; a steering knuckle having an upper end, a lower end, and a wheel supporting section between the upper end and the lower end, with the lower end pivotally coupled to the outboard side of the transverse link; a lower knuckle breakaway structure formed on the steering knuckle to release the steering knuckle from the transverse link upon application of a prescribed rearward directed force on the vehicle front suspension outboard of the lower suspension support structure; an upper suspension support structure; a strut having an upper end coupled to the upper suspension support structure, and a lower end coupled to the upper end of the steering knuckle; and an upper knuckle breakaway structure configured to release the steering knuckle from the strut upon application of the prescribed rearward directed force, such that at least the wheel supporting section is free from connection to the upper suspension support structure and the lower suspension support structure.
 11. The vehicle front suspension according to claim 10, wherein the lower knuckle breakaway structure includes a frangible portion formed on the steering knuckle.
 12. The vehicle front suspension according to claim 11, wherein the frangible portion is located between the wheel supporting section and the lower end of the steering knuckle, such that the upper end and the wheel supporting section are released from the lower end, and the lower end remains attached to the transverse link upon application of the prescribed rearward directed force.
 13. The vehicle front suspension according to claim 10, wherein the steering knuckle is coupled to the transverse link by a ball joint, and the lower knuckle breakaway structure includes a cam structure configured to release the ball joint upon rotation of the steering knuckle relative to the transverse link.
 14. The vehicle front suspension according to claim 13, wherein the cam structure of the lower knuckle breakaway structure comprises a first cam surface on the outboard side of the transverse link and a second cam surface on the lower portion of the steering knuckle, with the second cam surface travelling along the first cam surface to cause vertical movement of the steering knuckle relative to the transverse link as the steering knuckle rotates relative to the transverse link.
 15. The vehicle front suspension according to claim 14, wherein the ball joint is configured to break upon prescribed vertical movement of the steering knuckle relative to the transverse link.
 16. The vehicle front suspension according to claim 13, wherein the upper end, the lower end, and the wheel supporting section are free from connection to the transverse link upon release of the steering knuckle from the transverse link. 